$70 


NRLF 


B   M   S3D   MSS 


GIFT   OF 
Arthur  E.   Moncaster 


e 


Westinghouse-Parsons 
Steam  Turbine 


A  description, 

with  suggestions  and  instructions 
for  its 


INSTALLATION 

CARE  AND 

OPERATION 


ENGINEER'S  REFERENCE  BOOK 

Please   keep   this    book  where   your   engineer   can    refer 

to    it    readily 


Instruction  Book  WM  103 


The  West i  n  2h  ouse 


TFe 


Westinghouse-Parsons 
Steam  Turbine 


A  description, 

with  suggestions  and  instructions 
for  its 


INSTALLATION 

CARE  AND 

OPERATION 


EAST    PJTTSBUR.O,I>A. 


\i     J 


TABLE  OF  CONTENTS 

iHHH 

I. 

INTRODUCTION. 

II. 
THE  FUNDAMENTAL  PRINCIPLES  OF  A  STEAM  TURBINE. 

III. 
THE  WESTINGHOUSE-PARSONS  STEAM  TURBINE: 

ROTOR 

CYLINDER 

THRUST  BEARING 

MAIN  BEARINGS 

GLANDS 

GOVERNOR 

VALVE  GEAR 

OILING  SYSTEM 

AUTOMATIC  SAFETY  STOP 

AUTOMATIC  THROTTLE  VALVE 

COUPLING 

IV. 

OPERATING  SUGGESTIONS. 

V. 

CONDENSERS. 

VI. 

OILS. 

VII. 

METHODS  OF  CONNECTING  UP  GLANDS  AND  OIL  COOLING 

COILS. 

VIII. 
FOUNDATIONS. 


726306 


INTRODUCTION 

While  the  turbine  is  simple  in  design  and  construction, 
and  does  not  require  constant  tinkering  and  adjustment  of 
valve  gears,  or  taking  up  of  wear  in  the  running  parts,  it  is 
like  any  other  piece  of  fine  machinery,  in  that  it  should  receive 
intelligent  and  careful  attention  from  the  operator  by  inspection 
of  the  working  parts  that  are  not  at  all  times  in  plain  view. 
Any  piece  of  machinery,  no  matter  how  simple  and  durable,  if 
neglected  or  abused,  will  in  time  come  to  grief,  and  the  higher 
the  class  of  the  machine,  the  more  is  this  true. 

The  experienced  engineer  understands,  in  a  general 
way,  the  principles  and  operation  of  almost  any  piece  of 
apparatus  that  he  may  come  across  in  the  power  house.  At 
the  same  time  there  are  points  about  any  new  machine  that  he 
has  to  learn,  either  from  his  own  experience  or  the  previous 
experience  of  others,  and  the  latter  supplemented  and  confirmed 
by  the  former,  is  perhaps  apt  to  be  the  least  costly.  In  the 
case  of  the  ordinary  large  size  reciprocating  engine,  where  it  is 
almost  never  run  and  sometimes  not  even  assembled  in  the 
shop,  the  operating  engineer  can  often  tell  the  builders  more 
about  the  care  and  operation  of  the  engine  than  they  are  able 
to  tell  him;  but  in  the  case  of  the  turbine,  which  is  not  only 
assembled  but  is  thoroughly  tested  and  operated  for  some  time 
in  the  shop,  the  builders  have  had  continued  and  varied 
experience  under  all  sorts  of  conditions,  and  are,  therefore,  in  a 
position  to  give  advice  in  regard  to  its  operation  and  mainte- 
nance. 

The  object  of  this  pamphlet  is  to  cover  in  a  general 
manner  the  principal  features  of  construction  and  methods  of 
operation  common  to  all  Westinghouse  turbines,  the  details 
occasionally  met  with  in  special  types  being  described  in  a 
separate  pamphlet  covering  each  particular  case. 

5 


II. 

Fundamental  Principles  of  a  Steam  Turbine. 

Any  steam  turbine  depends  for  its  operation  upon  the 
effect  of  steaui  being  caused  to  expand  through  suitably  formed 
passages,  thereby  attaining  a  velocity.  The  steam  then 
impinging  upon  suitable  buckets  gives  up  the  energy  due  to 
velocity  and  thus  gives  motion  to  the  rotating  element  of  the 
turbine.  In  some  cases  the  steam  expands  through  passages 
which  are  themselves  capable  of  movement,  in  which  case  the 
effect  of  velocity  is  to  give  motion  to  the  rotating  element  by 
reason  of  reaction. 

In  the  Westinghouse-Parsons  turbine  use  is  made  of 
each  of  the  two  effects.  A  general  idea  of  the  turbine  blades 
may  be  gathered  from  the  diagram,  Fig.  i,  in  which  both 
stationary  and  moving  blades  are  shown  in  their  respective 
location  to  one  another. 


ELEMENT  A 


ELEMENT  B 


NARY  BLADES 


MOVING  BLADES 


J)  J)  J)  J)  J)  J  ))  D  )) 


BLADES 
BLADES 


Fig.  1 

The  steam  in  passing  through  row  i,  falls  from  pressure 
P  to  pressure  P^  In  thus  expanding  it  does  work  upon 
itself  and  attains  a  velocity,  the  energy  of  which  is  given  upon 
the  moving  blades,  row  2.  Again,  in  the  passage  of  steam 
through  the  blades  of  row  2,  the  pressure  falls  from  P:  to  P2. 
This  expansion  again  produces  a  velocity,  but  this  time  its 
effect  is  to  react  on  row  2.  This  cycle  is  repeated  a  number  of 
times  until  exhaust  pressure  is  reached. 


III. 

The  Westinghouse-Parsons  Steam  Turbine. 

Figure  2  is  a  sectional  view  showing  the  construction 
of  the  Westinghouse-Parsons  straight  parallel  flow  steam 
turbine.  While  the  different  types  vary  somewhat  in  minor 
details,  the  principle  of  operation  remains  the  same.  Steam 
enters  through  the  strainer  S,  passes  through  the  main 
admission  valve,  into  the  turbine  at  A.  After  expanding 
through  the  cylinders  Rx,  R2,  R3,  it  passes  down  the  exhaust 
chamber  D  to  the  condenser.  The  admission  of  steam  is 
regulated  by  the  valve  V  actuated  by  the  governor  G,  driven 
by  the  worm  wheel  at  the  end  of  turbine  rotor. 

There  are  two  distinct  types  of  steam  turbines  built  by 
the  Westinghouse  Machine  Company — the  straight  parallel 
flow  Westinghouse-Parsons  steam  turbine  as  shown  in  Figure  2, 
and  the  Double  Flow  Westinghouse  steam  turbine,  Figure  3. 
As  the  latter  is  a  development  of  the  former,  especially  suited 
for  handling  large  volumes  of  steam,  but  having  the  same 
elements  of  construction  such  as  rotor,  cylinder,  governor,  etc., 
and  is  operated  in  practically  the  same  manner,  it  is  treated  as 
a  special  case  and  the  details  of  design  such  as  direction  and 
regulation  of  flow  of  steam  are  discussed  in  a  separate 
pamphlet. 

The  principal  elements  of  construction  are  taken  up  as 
follows : 

Rotor: 

This  is  shown  at  R,  P,  Figure  2.  The  parts  Rx,  R2, 
R3,  consist  of  steel  drums  mounted  upon  a  spindle,  in  which 
are  inserted  rows  of  blades  or  vanes,  by  means  of  which  the 
rotative  effort  imparted  by  the  steam  is  received  and  transmitted 
to  the  rotor.  On  the  opposite  end  of  the  spindle  and  corre- 
sponding to  each  diameter,  R,  are  balance  pistons  Pj,  P2,  P3, 
of  such  diameter  as  to  exactly  balance  the  axial  pressure  on  the 
drums  R1?  R2,  R3,  the  different  pressures  at  either  end  of  the 
respective  drum  diameter  being  communicated  to  the  corre- 


10 


spending  piston  faces  by  means  of  the  passages  EI,  E2,  Es, 
as  shown.  These  balance  pistons  have  a  number  of  grooves 
cut  in  their  faces,  into  which  mesh  corresponding  collars  in  the 
cylinder,  thereby  effectively  preventing  leakage,  although  they 
run  without  actual  metallic  contact. 

Cylinder: 

The  rotor  revolves  in  the  stator  or  stationary  cylinder, 
which  has  rows  of  guide  blades  corresponding  to  those  in  the 
spindle,  but  set  in  reverse  position.  (See  Fig.  i.)  Also  placed 
in  the  cylinder,  at  the  section  occupied  by  the  balance  piston, 
are  collars  or  strips,  which  fit  into  the  grooves  in  the  balance 
pistons  on  the  spindle  as  referred  to  above.  By  means  of 
aligning  bearings,  TT,  T2,  Figure  2,  the  spindle  is  held  in 
such  a  position  that  the  sides  of  the  grooves  in  the  balance 
piston  are  close  to  the  strips  in  the  cylinder,  but  not  close 
enough  to  touch  them,  thus  preventing  the  passage  of  any 
appreciable  amount  of  steam  without  rubbing  contact  between 
the  adjacent  surfaces. 

Referring  again  to  Figure  2,  which  represents  the 
typical  Westinghouse-Parsons  turbine  in  sizes  from  300  to 
3000  Kw.,  it  will  be  noticed  that  there  are  three  large  changes 
in  the  diameter  of  the  working  portions  of  the  spindle  and 
cylinder.  These  are  commonly  referred  to  as  the  different 
cylinders  of  the  turbine,  being  respectively  the  high  pressure, 
the  intermediate  pressure  and  the  low  pressure  cylinders, 
starting  with  the  smallest  diameter  at  RI,  R_>  being  the  inter- 
mediate and  R3  the  low  pressure  cylinder.  It  will  be  noticed 
that  each  cylinder  is  further  divided  into  small  steps,  each  one 
of  these  latter  having  blade  rows  of  the  same  height.  Each  of 
these  steps  is  known  as  a  barrel,  there  being  usually  three  to 
five  of  these  in  each  of  the  cylinders,  and  anywhere  from  one 
to  twenty  rows  in  each  of  these  barrels.  In  the  event  of  any 
correspondence  relating  to  blading,  it  is  customary  to  refer  to 
any  particular  row  of  blades  as  the  ist,  2d,  3d,  or  otherwise 
row  in  the  ist,  2d,  3d  or  otherwise  barrel  in  the  high  pressure, 
intermediate  or  low  pressure  cylinder  of  the  spindle  or  cylinder, 
as  the  case  may  be,  counting  from  the  high  pressure  end. 

11 


12 


Thrust  Bearing: 

The  aligning  or  thrust  bearing  is  made  up  of  two  parts 
T!,  T>,  each  consisting  of  a  cast  iron  body  in  which  are  placed 
brass  collars.  (See  Fig.  4.)  These  collars  fit  in  grooves  C,  cut 
in  the  shaft  as  shown.  The  halves  of  the  block  are  brought 
into  position  by  means  of  screws  Si,  S2,  acting  on  levers  Li> 
1,2,  mounted  in  the  bearing  pedestal  and  cover.  It  will  be 
seen  that,  by  turning  the  screw  inwards,  the  half  of  the  block 
that  it  acts  on  is  moved  in  the  opposite  direction,  and  that 
the  spindle  cannot  move  beyond  that  point. 

The  screws  are  provided  with  graduated  heads,  which 
permit  the  position  of  the  respective  halves  of  the  thrust  bear- 
ing to  be  set  to  one-thousandth  of  an  inch.  The  arrangement 
of  each  screw  is  similar  to  the  familiar  micrometer. 

The  upper  screw  S2,  is  set  so  that  when  the  rotor  exerts 
a  light  pressure  against  it,  the  grooves  in  the  balance  pistons 
just  escape  coming  in  contact  with  the  strips  in  the  cylinder. 
The  lower  screw  Si,  is  adjusted  to  permit  about  eight  one- 
thousandths  to  ten  one-thousandths  of  an  inch  freedom  for  the 
collars  C,  between  the  thrust  bearings. 

The  alignment  bearings  are  carefully  adjusted  before 
the  machine  leaves  the  shop  and,  to  prevent  either  accidental 
or  unauthorized  changes  of  their  adjustment,  the  adjusting 
screw  heads  are  locked  by  the  method  shown  in  Figure  4.  It 
will  be  observed  that  the  screw  cannot  be  revolved  without 
sliding  back  the  latch  L3.  To  do  this  the  pin  P4,  must  be 
withdrawn,  for  which  purpose  the  bearing  cover  must  be 
removed. 

In  general,  this  adjustment  should  not  be  changed 
except  in  some  special  case  where  there  has  been  wear  of  the 
collars  in  the  alignment  bearings.  Nevertheless,  it  is  a  wise 
precaution  to  go  over  the  adjustment  at  intervals.  The  method 
of  doing  this  is  usually  as  follows:  The  machine  should  have 
been  in  operation  for  some  time  so  as  to  be  well  and  evenly 
heated  and  should  be  run  at  a  reduced  speed,  say  10%  of  the 
normal  speed,  during  the  actual  operation  of  making  the  adjust- 
ment. Adjust  the  screw,  which,  if  tightened,  would  push  the 

13 


spindle  away  from  the  thrust  bearing  towards  the  exhaust. 
This,  in  some  type  of  machines  might  be  the  upper  screw  and 
in  others  the  lower  screw;  as  shown  in  Figure  4  it  is  the  upper 
screw.  Find  a  position  for  this,  such  that,  when  the  lower 
screw  is  tightened,  thus  drawing  the  spindle  towards  the 
governor  end,  the  balance  pistons  can  just  be  heard  coming  in 
contact,  and  such  that  the  least  change  of  position  inwards  of 
the  upper  screw  will  cause  the  contact  to  cease  by  forcing  the 
spindle  towards  the  exhaust  end  as  evident  from  Figure  2. 
To  hear  if  the  balance  pistons  are  in  contact,  a  short  piece  of 
hard  wood  should  be  placed  against  the  cylinder  casing  near 
the  balance  pistons.  If  one's  ear  is  applied  to  the  other  end  of 
the  piece  of  wood,  the  balance  pistons  can  be  heard  when  in 
contact  with  the  strips  in  the  cylinder.  The  lower  screw 
should  then  be  loosened  and  the  upper  screw  advanced  six  one- 
thousandths,  at  which  position  the  latter  may  be  considered  to 
be  set.  The  lower  screw  should  then  be  advanced  until  one- 
half  of  the  thrust  pushes  the  rotor  against  the  other  half  of  the 
thrust  bearing,  and  from  this  position  it  should  be  slacked 
back  ten  one-thousandths  to  give  freedom  for  the  rotor  between 
the  thrusts  and  locked. 

Great  care  must  be  exercised  in  this  operation,  in 
determining  when  the  collars  of  the  balance  pistons  are  just  in 
contact.  Gentle  pressures  only  must  be  exerted  in  adjusting 
these  screws  or  the  parts  will  be  strained,  giving  an  erroneous 
setting.  This  contact  should  be  only  momentary,  and  the 
screw  should  be  released  just  as  soon  as  the  rubbing  is  heard. 

The  above  mentioned  dimensions  of  clearance  apply 
only  to  turbines  up  to  1000  Kw.  Special  settings  are  generally 
used  in  larger  sizes. 

The  object  in  view  is  to  have  the  grooves  of  the  balance 
pistons  running  as  close  as  possible  to  the  collars  in  the 
cylinder,  but  without  danger  of  their  coming  in  actual  contact 
and  to  allow  as  little  freedom  as  possible  in  the  thrust  bearing 
itself,  but  enough  to  be  sure  that  it  will  not  heat.  The  tur- 
bine rotor  itself  has  scarcely  any  end  thrust,  so  that  all  the 
thrust  bearing  has  to  do  is  to  maintain  the  above  described 
adjustment. 

14 


Some  machines  are  provided  with  a  thrust-bearing, 
having  both  adjusting  screws  on  the  upper  cap,  facilitating  the 
operation  of  adjusting  the  thrust  blocks.  However,  the 
same  precautions  and  directions  given  in  connection  with 
Figure  4,  apply  to  this  bearing,  as  it  differs  only  in  arrange- 
ment of  details. 

The  principal  feature  wherein  it  differs  from  Figure  4  is 
the  position  of  lever  for  adjusting  the  lower  half  of  the  bear- 
ing. Instead  of  engaging  in  the  bottom  of  the  bearing  and 
requiring  adjustment  in  the  lower  part  of  the  pedestal,  the 
lever  consists  of  two  arms  which  span  the  upper  bearing  and 
engage  in  recesses  at  the  side  of  the  lower  bearing  so  that  it  is 
adjusted  from  above.  The  two  adjustment  screws  are  so 
located  that  both  may  be  conveniently  regulated  at  the  same 
time,  by  adjusting  one  with  either  hand.  In  most  cases  the 
inner  adjustment  screw,  that  is  the  one  nearer  to  the  turbine 
casing,  controls  the  upper  thrust  block,  while  the  outer  regu- 
lates the  lower  block. 

The  lock  slide  (L3)  is  held  in  place  by  a  screw  which 
in  turn  is  prevented  from  becoming  loose  by  being  drilled  to 
receive  two  cotter  pins,  one  on  each  side  of  the  slide. 

Main   Bearings: 

The  bearings  which  support  the  rotor  of  the  smaller 
machines  running  at  3,600  r.  p.  m.  are  shown  at  B,  B,  Fig.  2, 
and  in  detail  in  Fig.  5.  The  bearing  proper  consists  of  a  brass 
tube,  B,  Fig.  5,  with  suitable  oil  grooves.  It  has  a  dowel  arm 
L,  which  fits  into  a  corresponding  recess  in  the  bearing  cover, 
to  prevent  the  bearing  from  turning.  Around  this  tube  are 
three  concentric  tubes,  C,  D,  E,  each  one  fitting  over  the  other 
with  some  clearance,  so  that  the  bearing  itself  is  free  to  move 
slightly  in  any  direction.  These  tubes  are  held  in  place  by 
the  nut  F,  and  this  nut  in  turn  is  held  by  the  small  set  screw 
G.  The  bearing  with  the  surrounding  tubes  is  placed  inside 
of  the  cast  iron  shell  A,  which  rests  in  the  bearing  pedestal  on 
the  blocks  and  liners  H.  The  packing  ring  M,  prevents  the 
leakage  of  oil  past  the  bearing.  Oil  enters  the  chamber  at  one 

15 


16 


end  of  the  bearing  and  passes  through  the  oil  grooves  lubri- 
cating the  journal,  and  then  out  into  the  reservoir  under  the 
bearing.  The  oil  also  fills  the  clearance  between  the  tubes 
and  forms  a  cushion  which  dampens  any  slight  vibra- 
tions. The  bearings,  therefore,  absorb  any  vibration  that 
might  occur. 

In  some  cases  the  bronze  tube  B  is  lined  with  babbitt, 
giving  a  babbitt  bearing  surface,  while  the  rest  of  the  bearing 
parts  remain  the  same. 

This  type  of  bearing  with  its  nest  of  tubes  is  required 
only  in  high  speed  machines  where  the  bodies  revolve  above 
the  critical  speed,  the  tubes  permitting  the  revolving  element 
to  tend  to  revolve  about  its  gravity  axis  rather  than  about  its 
geometric  axis.  The  results  are  the  same  as  were  obtained 
later  by  Dr.  De  Laval  by  means  of  his  flexible  shaft. 

In  the  larger  machines  running  at  1,800  r.  p.  m.  or  less, 
a  babbitted  bearing  is  usually  employed.  This  type  of  bearing 
is  shown  in  Fig.  6,  being  divided  longitudinally  in  the 
usual  manner.  It  is  also  self-aligning,  and  is  supplied  with 
oil  at  the  center  through  suitable  passages,  discharging  at 
each  end. 

This  bearing  consists  of  two  cast  iron  shells,  A  and  B, 
Fig.  6,  lined  with  babbitt  and  held  together  by  the  bolts  C  C 
and  supported  by  the  blocks  and  liners  H.  H.  The  babbitt  is 
bored  out  slightly  larger  than  the  shaft,  and  further  bored 
along  the  sides  so  that  the  horizontal  dimension  of  the  bore  is 
somewhat  greater  than  the  vertical,  thus  giving  close  contact 
along  only  about  two-thirds  of  the  bottom  half  of  the  circum- 
ference, allowing  ample  room  for  oil  to  produce  perfect  lubri- 
cation. The  oil  enters  at  the  point  D  and  passes  around  the 
passages  E,  E,  coming  into  the  bearing  at  F. 

The  outer  shells  of  both  types  of  bearings  are  provided 
with  four  recesses,  in  which  are  fitted  keys,  as  shown  at  H,  upon 
which  the  bearing  is  carried  in  the  pedestal.  These  keys  have 
a  number  of  sheet  metal  liners  behind  them  by  means  of  which 
accurate  adjustment  may  be  made  of  the  bearings  to  give  any 
desired  adjustment  of  the  revolving  part  with  reference  to  the 

17 


Fig.  6 


18 


stationary  part.  These  liners  are  arranged  in  combinations  to 
permit  adjustments  to  be  made  in  increments  of  five  one- 
thousandths  of  an  inch. 

Glands: 

On  either  end  of  the  turbine  spindle  at  W  W,  Fig.  2, 
are  located  the  water  sealed  glands  to  prevent  air  leaking  into 
the  turbine  when  running  condensing  and  to  prevent  steam 
blowing  out  when  operating  with  atmospheric  or  greater  press- 
ure at  the  exhaust. 

Referring  to  Fig.  7,  the  sealing  water  is  supplied  to  the 
glands  through  passage  A  in  the  turbine  casing  to  chamber 
B,  in  which  the  runner  C  revolves  with  the  turbine  shaft. 
This  runner  is  designed  to  be  capable  of  pumping  to  a  pressure 
of  about  thirty-five  pounds  if  it  were  furnished  with  water  at 
its  inner  radius,  so  that  when  water  is  supplied  to  its  periphery 
at  twenty  pounds  absolute,  or  say  twenty  pounds  greater  than 
the  pressure  within  the  turbine,  this  water  is  unable  to  flow 
into  the  turbine  by  reason  of  the  pumping  effect  of  the  gland 
runner  in  the  opposite  direction.  Thus  there  is  maintained  at 
the  outer  edge  a  solid  annulus  of  water  of  a  pressure  greater 
than  the  pressure  the  gland  has  to  pack  against,  producing  a 
hermetic  seal  entirely  precluding  the  passage  of  air. 

The  spindle  gland  sleeve  E,  which  is  shrunk  on  the 
shaft  and  doweled  at  H,  consists  of  a  bronze  ring  provided  with 
grooves.  This  gland  sleeve  has  a  running  clearance  between 
it  and  the  casing  F,  and  acts  as  a  labyrinth  packing  to  prevent 
excessive  leakage  along  the  shaft  while  the  turbine  is  operat- 
ing slowly.  What  slight  leakage  there  may  be  is  taken  care 
of  by  the  drain  pipe  K.  This  should  be  a  free  drain,  and  at 
all  times  maintained  clear,  otherwise  water  may  leak  through 
the  oil  ring  into  the  bearing  chamber,  and  contaminate  the 
oiling  system. 

A  pipe  G  is  provided  at  the  inner  side  of  the  gland  for 
the  purpose  of  draining  away  any  leakage  to  the  exhaust  pipe 
and  preventing  it  from  splashing  on  the  revolving  rings  of  the 
turbine. 

19 


20 


The  outer  flange  is  to  prevent  any  leakage  from  the 
shaft  being  thrown  off  into  the  engine  room. 

A  gauge  at  D  indicates  the  pressure  at  the  outer  edge 
of  the  glands,  so  that  it  may  be  known  whether  or  not  the 
water  supply  is  being  properly  maintained. 

Suggestions  regarding  various  methods  of  connecting 
the  water  supply  to  these  glands  are  given  in  the  latter  part  of 
this  pamphlet. 

In  the  case  of  low  pressure  turbines  where  it  is  neces- 
sary to  obtain  a  vacuum  before  the  spindle  is  revolved,  a  special 
type  of  gland  is  furnished,  as  described  elsewhere,  in  connec- 
tion with  low  pressure  turbines. 

Governor : 

Fig.  8  shows  a  section  of  the  Westinghouse-Parsons 
flyball  type  of  governor  used  in  conjunction  with  poppet  valves 
and  steam  relay  mechanism  for  controlling  the  admission  of 
steam. 

Keyed  on  the  end  of  the  turbine  shaft  is  a  steel  worm 
driving  the  bronze  worm  wheel  A.  This  gear  A  drives  the  oil 
pump  crank  C  and  transmits  its  motion  by  means  of  a  bevel 
gear  and  pinion  to  the  governor  spindle,  D.  On  this  spindle 
is  keyed  the  governor  arm  which  carries  the  balls  W  W,  the 
levers  N  N  being  mounted  on  knife  edge  pins.  On  the  ends 
of  these  levers  are  rollers  which  support  a  roller  ring  and  ball 
race  upon  which  the  governor  spring  S  acts.  The  object  of 
this  arrangement  is  to  allow  adjustment  of  the  governor  while 
the  turbine  is  running;  by  lightly  grasping  the  sleeve  locking 
plate  G,  the  tension  sleeve,  spring  and  spindle  sleeve  collar 
are  brought  to  rest,  and  the  governor  balls  are  still  free  to 
revolve  on  the  above  mentioned  ball  thrust  bearing. 

Therefore,  to  vary  the  speed  of  the  turbine,  hold  the 
tension  sleeve  nut  G  with  one  hand,  and  with  the  other  loosen 
the  locknut  K  a  sufficient  amount  to  disengage  the  pin  in  the 
locking  plate  from  slot  in  G.  Then  adjust  the  sleeve  nut  until 
the  speed  has  been  changed  the  desired  amount.  In  this 
manner  adjustments  of  speed  are  made  without  interfering 

21 


GOV. SPINDLE  CAP 

QOV.TENSION  SLEEVE 

GOV. TENSION   SLEEVE  LOCK  NUT 

GOV.TENSION  SLEEVE  LOCKING  PLATE 

QOV.TENSION  SLEEVE  NUT 

GOV.  CASE 
GOV. BALL  LEVER 

GOV.CASE  STAND 
GOV.CLUTCH  SLEEVE  RING, UPPER 

GOV.ROCKER  ARM  — 
GOV.ROCK  SHAFT  BRACKET  CAP 

GOV.CLUTCH  LEVER  LINK 

GOV.CLUTCH  DISTANCE  PIECE 

GOV.CLUTCH  SLEEVE  RING. LOWER 

GOV.ROCK  SHAFT  BRACKET 

GOV.CLUTCH  SLEEVE  NUT 

GOV.STARTING  TRIGGER 

GOV.STARTING  TRIGGER  BRACKET 

GOV.SPINDLE  BUSHING.UPPER 

GOV.  SPINDLE 
GOV.THRUST  BEARING  RING.UPP 

"       INTERMEDIATE 
..       LOWER 

GOV. SPINDLE  BUSHING, LOWER 
GOV. BEVEL  PINION 

GOV.SPINDLE  WASHER 

GOV.WORM  WHEEL   SHAFT  CAP 

GOV.WORM  WHEEL   SHAFT  BUSHING, SMALL 

GOV.  BEVEL  GEAR 


SECONDARY   LEVER 


GOV.SPRING 

GOV.SPINDLE  SLEEVE 

GOV.SPINDLE  SLEEVE  COLLAR 

GOV.  BALL  RETAINER  RING 

GOV.  ROLLER  RING 
GOV.  KNIFE  EDGE  PIN  I  BLOCK 

GOV.ARM 
GOV.ROLLER  E.  PIN 

GOV.  CONNECTING  LINK 

GOV.CLUTCH  SLEEVE 
GOV.DASH  POT  LEVER 
GOV.DASH  POT  CLUTCH 

GOV.CLUTCH 
.VIBRATOR  ROD  LINK 
GOV.CLUTCH  LEVER 
GOV.VIBRATOR  ROD  GUIDE 

GOV.YOKE 
COV.VIBRATOR  ROD   BUSHING, UPPER 

IV.VIBRATOR  ROD 
GOV.VIBRATOR   SPRING 
QOV.VIBRATOR  SPRING  SLEEVE 
GOV.VIBRATOR  ROD  BUSHING, LOWER 
GOV.GEAR  CASE 
OV.VIBRATOR  ROLLER 
GOV.VIBRATOR  ROLLER  BUSHING 
GOV.VIBRATOR   ROLLER  PIN 

WHEEL  SHAFT  BUSHING, LARGE 


GOV.VIBRATOR   CAM 
OV.WORM  WHEEL  SHAFT 

L  PUMP  CRANK 
-GOV.WORM  WHEEL 
GOV.WORM 


Fig.  8 


22 


with  the  operation  of  the  turbine.  This  spring  adjustment 
may  be  used  if  desired  for  bringing  one  machine  into  syn- 
chronism with  another  or  for  transferring  the  load  to  or  from 
other  turbines  operating  in  parallel. 

Of  course  the  spring  tension  may  be  changed  while  the 
turbine  is  at  rest,  but  it  cannot  be  set  at  any  definite  speed 
unless  the  nuts  have  been  previously  marked  for  certain 
settings. 

The  oscillatory  motion  of  the  valves  is  derived  from  a 
cam  or  eccentric  on  the  worm  wheel  shaft  operating  the  vibra- 
tor rod  which  in  turn  actuates  the  clutch  lever  F,  which  is 
pivoted  on  the  governor  clutch.  This  clutch  is  free  to  travel 
on  the  spindle  in  response  to  different  positions  of  the  governor 
balls  and  levers.  The  effect  of  a  change  in  the  position  of  the 
governor  weights  is  merely  to  change  the  plane  of  oscillation 
of  the  clutch  lever,  since  the  amplitude  of  the  oscillations 
remains  constant.  The  clutch  lever  is  connected  by  means  of 
suitable  arms  to  the  relay  plunger  which,  while  constantly 
oscillating,  changes  its  mean  position  in  accordance  with 
changes  in  the  position  of  the  governor  balls,  or  in  other 
words,  in  accordance  with  the  demands  of  the  load.  The  oper- 
ation of  this  relay  plunger  and  manner  in  which  it  regulates 
the  inlet  of  steam  is  explained  on  page  27  and  following. 

The  motion  of  the  clutch  is  dampened  by  means  of  a 
dash  pot  connected  by  levers  pivoted  at  I. 

The  starting  trigger  M  holds  the  lever  in  the  position 
corresponding  to  normal  speed,  so  that  the  relay  plunger  will 
allow  the  primary  valve  to  open.  It  should  fall  out  of  place 
as  soon  as  the  turbine  attains  normal  speed  and  the  governor 
weights  regulate  the  position  of  the  valve  mechanism. 

Fig.  9  shows  a  sectional  view  of  another  type  of  gover- 
nor. 

The  governor  spindle  F  is  driven  directly  from  the 
worm  S  on  the  end  of  the  turbine  shaft,  meshing  with  the 
worm  wheel  V.  This  spindle  carries  the  governor  arm  on 
which  the  weights,  two  cast  iron  blocks  of  rectangular  cross 
section,  are  supported  by  means  of  levers  and  parallel  guide 

23 


WEIGHTS 


GOV.  SPRING  RETAINER 

OOV.  WEIGHT  GUIDE  LINK 
GOV.  ARM 

CLUTCH  LEVER  BALL  B*RG 

(c 


VIBRATOR  ROD 
GOV  WOR 


VIBRATOR  CAM  GEAR 


r-  GOV.  SPRING  ADJUSTING  SCREW 

»»»»»»          NUT 


GOV.  WEIGHT  LEVERS 


SPINDLE  THRUST  BEARING  RINGS 


OIL  INLET  TO  SPINDLE 
OV.  CLUTCH 

LEVER 


CLUTCH  LEVERBRACKET 


DASH  POT 


— E^Sf-OOV.  SPINDLE  BEARING 

^     ff 

~|p--OOV.  SPINDLE 

^SPINDLE  BUSHING 

tN1"?.-; 

V.  WORM  WHEEL 


VIBRATOR  CAM  PINION 


Fig.  9 


24 


links  T.  When  the  turbine  is  at  rest  the  weights  are  in  their 
innermost  position  and  the  clutch  A  at  its  lowest  position,  and 
therefore  the  relay  plunger  is  raised  to  such  a  position  as  to 
admit  steam  to  the  turbine,  as  explained  in  the  discussion  of 
the  valve  setting.  As  the  turbine  is  brought  up  to  speed  the 
centrifugal  force  of  the  weights  is  resisted  by  the  spring  R 
directly  opposing  this  force  through  the  axis,  and  thus  no 
stresses  are  transmitted  through  the  governor  levers. 

The  lower  end  of  the  governor  spindle  carries  a  pinion, 
meshing  into  a  larger  gear  C,  which  operates  the  oil  pump 
below.  The  upper  surface  of  this  gear  carries  a  cam,  operating 
the  vibrator  rod,  which  is  maintained  against  the  face  of  the 
cam  by  means  of  the  spring  shown  in  the  illustration. 

The  tension  of  the  governor  spring  may  be  adjusted  by 
means  of  the  adjusting  screw  K,  which  acts  on  the  spring 
shackles,  the  latter  being  constructed  so  that  a  number  of  coils 
of  the  spring  may  be  thrown  in,  or  out  of  action  as  desired. 
Thus,  the  speed  at  which  the  governor  will  regulate  may  be 
adjusted  by  the  adjusting  screws,  and  if  it  is  desired  to  increase 
the  speed  variation  between  different  loads,  the  spring  may  be 
shackled  up,  cutting  coils  out  of  action,  or  vice  versa,  to  make 
the  speed  variation  less  with  changes  of  load  more  coils  may 
be  thrown  into  action.  Such  adjustments,  however,  are  always 
made  at  the  time  the  turbines  are  tested,  and  no  further  adjust- 
ment should  be  necessary. 

This  governor  differs  from  the  one  previously  described 
in  that  the  spring  cannot  be  adjusted  while  the  turbine  is  in 
operation,  and  hence,  an  auxiliary  spring  is  required.  The 
combined  adjustment  of  the  springs  should  permit  the  speed 
of  the  turbine  to  be  lowered,  say  5%,  by  means  of  the  auxiliary 
spring,  or  enough  so  that  the  turbine  may  always  be  syn- 
chronized when  being  started  up.  Therefore,  the  main  gover- 
nor spring  should  have  an  adjustment  such  that  with  the 
machine  shut  down  and  the  weights  in  their  innermost  posi- 
tion, the  auxiliary  spring  having  substantially  no  tension, 
the  turbine  will  run  with  no  load,  and  be  under  control  of  the 
governor  at  5%  below  speed.  Then,  by  means  of  the  auxiliary 

25 


26 


spring,  the  speed  may  be  brought  up  to  normal,  when  the  tur- 
bine should  have  a  speed  variation  between  no  load  and  normal 
load,  in]  [accordance  with  the  requirements  of  the  particular 
service  to  which  it  is  applied. 

With  this,  as  much  as  with  any  governor,  it  is  always 
essential  that  the  main  valve  shall  come  to  its  closed  position 
before  the  governor  weights  are  in  their  outermost  position. 

It  is  to  be  noted  that  oil  from  the  main  oiling  system  is 
admitted  between  the  two  spindle  bushings,  from  which  point 
suitable  passages  lead  it  to  every  part  of  the  governor  requir- 
ing lubrication.  The  weight  of  the  governor  is  carried  on  the 
thrust  bearing  rings  M.  These  rings  receive  a  liberal  supply 
of  oil  from  the  spindle  bushing,  the  surplus  passing  on  to  the 
surface  of  the  clutch  A.  Oil  also  passes  to  the  interior  of  the 
spindle  and  out  through  the  tubes  P,  lubricating  the  joints  of 
the  governor  weight  levers. 

One  feature  of  this  governor  is  that  the  clutch  sleeve 
revolves,  being  driven  by  the  governor  weight  levers.  It 
revolves,  however,  on  a  stationary  portion,  thus  rendering  it 
frictionless,  in  so  far  as  any  vertical  sliding  motion  is  concerned. 

Valve  Gear: 

Figure  10  shows  a  section  through  the  valve  chamber 
of  a  Westinghouse-Parsons  steam  turbine  fitted  with  its  valves 
and  relay  plungers  for  governing  the  admission  of  steam. 

By  means  of  a  rockshaft  and  system  of  levers  connected 
to  the  governor  clutch  lever,  an  oscillatory  motion  is  com- 
municated to  the  relay  plungers  F  and  P,  which  operate  the 
primary  and  secondary  admission  valves  Vi  and  V2,  Figure  2. 
The  primary  valve  regulates  between  no  load  and  slightly  over 
full  load,  and  then  the  secondary  valve  automatically  comes 
into  operation  enabling  the  turbine  to  carry  high  overload  with 
normal  operating  conditions,  or  full  load  without  a  vacuum. 

The  action  of  these  relay  plungers  is  shown  in  detail  in 
Figure]  10.  If  the  throttle  valve  be  opened  with  the  relay 
plunger  F  in  the  position  shown,  steam  will  pass  up  through 
the  small  port  A  to  the  space  beneath  the  piston  C, — the 

27 


amount  of  steam  being  regulated  by  the  needle  valve  B.  As 
the  exhaust  through  the  port  E  is  closed  by  the  relay  plunger 
and  the  upper  side  of  the  piston  C  is  subjected  to  atmospheric 
pressure  only,  the  steam  pressure  beneath  raises  the  piston 
compressing  the  spring  H,  thus  lifting  the  valve  from  its  seat, 
and  admitting  steam  to  the  turbine  at  V.  While  the  plunger 
is  oscillating  in  this  position,  the  oscillations  are  not  great 
enough  to  uncover  the  port  E.  However,  the  outward  motion 
of  the  governor  weights  will  cause  the  plunger  to  move  to  a 
lower  mean  position  such  that  the  oscillations  will  uncover  the 
port  E  and  exhaust  more  or  less  of  the  steam  from  below  the 
piston,  and  the  valve  will  be  closed  correspondingly  by  the 
spring  H.  Violent  closing  of  the  valve  is  prevented  by  the 
dash  pot  piston. 

While  the  plunger  is  oscillating  with  a  constant  ampli- 
tude the  opening  of  the  port  E  varies  in  accordance  with  the 
position  of  the  governor.  At  light  loads,  no  more  pressure 
accumulates  beneath  the  piston  than  is  sufficient  to  just  raise 
the  valve  Vi  off  its  seat  at  each  oscillation.  As  the  load  in- 
creases the  valve  will  have  an  increasing  lift,  admitting  steam 
to  the  turbine  in  puffs, — until  at  maximum  load  these  puffs 
merge  into  a  continuous  blast,  and  the  valve  is  practically  sta- 
tionary in  its  wide  open  position. 

There  are  several  advantages  arising  from  the  use  of 
this  puff  system  of  steam  admission, — 

ist.  Inasmuch  as  the  valve  is  continually  moving  it 
never  can  become  stuck  in  one  position, — any  tendency  to 
sticking  will  be  apparent  at  once  and  may  be  rectified. 

2nd.  In  effect  this  valve  wiredraws  the  steam,  and  if  it 
were  in  a  fixed  position  the  seats  would  cut  out  rapidly  during 
times  of  light  load.  This  wire  drawing  effect  is  practically 
eliminated  because  at  reasonably  fractional  loads  the  valve 
virtually  opens  wide  at  its  up  stroke,  when  there  is  no  wiredraw- 
ing, and  reaches  its  seat  and  is  closed  on  the  down  position. 
It  might  be  approximately  said  that  at  light  loads  the  valve  is 
closed  the  greater  part  of  the  time  of  an  oscillation  and  open  but 
a  small  part.  At  heavier  loads  it  is  open  the  greater  part  of  the 

28 


time  and  closed  but  a  small  portion.  Hence  the  wiredrawing  is 
much,  less  than  if  the  valve  were  in  a  fixed  position. 

3rd.  Inasmuch  as  the  valve  admits  puffs  of  high  pres- 
sure steam,  the  walls  of  the  cylinder  assume  temperatures  cor- 
responding to  the  higher  pressures, — so  an  increase  of  load 
practically  merely  increasing  the  duration  of  the  puffs  will  af- 
fect the  temperature  condition  of  the  turbine  cylinder  less  than 
if  the  increase  of  load  required  an  increase  of  steam  pressure  as 
in  the  case  of  a  wiredrawing  method  of  steam  admission. 

It  will  be  seen  that  the  secondary  valve  is  slightly  dif- 
ferent in  its  action.  As  this  valve  is  in  operation  only  when 
there  is  an  overload  on  the  turbine,  it  may  not  be  brought  into 
action  for  comparatively  long  periods.  In  order  that  the  relay 
mechanism  may  not  consume  steam  during  such  periods,  it  is 
so  constructed  that  the  relay  plunger  does  not  begin  to  exhaust 
steam  until  such  time  as  the  operation  of  the  secondary  valve 
is  required.  Steam  is  admitted  to  both  sides  of  the  piston  N 
through  the  needle  valves  M  M,  and  when  on  account  of  in- 
creased load  the  mean  position  of  the  relay  plunger  P  is  raised 
sufficiently  by  the  governor,  the  port  O  is  opened,  exhausting 
the  steam  from  the  upper  side  of  the  piston,  and  the  valve 
lifts  by  reason  of  the  greater  pressure  beneath  the  piston  N. 
The  port  O  may  be  permanently  closed  by  the  hand  valve  Q, 
on  the  side  of  the  secondary  relay  steam  chest,  thus  cutting 
the  secondary  valve  entirely  out  of  action.  The  spring  R  acts 
in  a  similar  way  to  PI  in  the  main  valve.  The  end  of  the  sec- 
ondary valve  stem  shows  in  the  gauge  glass  S,  so  that  it  can 
be  readily  seen  whether  or  not  the  valve  is  operating  properly, 
or  that  it  remains  shut  all  of  the  time  when  its  operation  is 
not  required. 

There  are  two  needle  valves  for  the  purpose  of  regulat- 
ing the  action  of  the  primary  poppet  valve.  The  one  on  the 
dash  pot  is  merely  for  the  purpose  of  checking  the  drop  of  the 
valve  and  needs  no  comment.  The  lower  one,  B,  on  the  relay 
steam  cylinder  controls  the  inlet  of  the  steam  to  the  bottom  of 
the  piston.  If  this  valve  is  not  opened  to  pass  sufficient  steam, 
the  result  will  be  that  the  main  valve  will  not  be  raised  to  its 

29 


extreme  lift  and  the  machine  will  be  unable  to  carry  maximum 
load.  If  too  wide  open,  the  valve  will  operate  with  unneces- 
sary violence,  and  if  opened  to  admit  an  inordinate  amount  of 
steam,  the  valve  will  fail  to  close  effectively  when  it  is  called 
upon  to  do  so,  because  the  volume  of  the  steam  will  be  so 
great  that  it  cannot  be  completely  exhausted  by  the  relay 
plunger  F. 

The  functions  of  the  needle  valves  M,  M,  on  the  second- 
ary valve  are  somewhat  different.  The  lower  needle  valve 
admits  steam  below  and  the  upper  one  above  the  operating 
piston.  The  effect  of  the  relay  plunger  is  to  release  the  pres- 
sure above  the  piston  when  the  valve  is  required  to  open.  The 
lower  needle  valve  should  be  opened  no  wider  than  is  just 
necessary  to  allow  the  secondary  valve  to  open  freely  when 
the  relay  plunger  releases  the  pressure  above  the  piston. 
The  upper  needle  valve  should  be  open  sufficiently  to  prevent 
the  valve  from  being  lifted  from  its  seat  at  full  load  or  less,  by 
the  puffs  of  steam  within  the  turbine.  At  the  same  time  this 
needle  valve  must  not  be  opened  too  much,  or  steam  will  not 
be  released  freely  enough  by  the  relay  plunger  to  permit  the 
poppet  valve  to  open  when  it  is  called  upon  to  do  so.  The 
upper  valve  should  not,  however,  be  opened  very  much  wider 
than  the  lower  valve,  as  when  the  pressure  drops  with  each 
impulse  of  steam  admitted  by  the  primary  valve,  the  pressure 
on  top  of  the  piston  will  decrease  faster  than  below,  on  account 
of  the  freer  communication  with  the  interior  of  the  turbine, 
causing  the  valve  to  lift  slightly.  The  bobbing  of  the  valves 
on  light  loads  may,  therefore,  usually  be  remedied  by  changing 
the  relative  opening  of  the  two  valves ;  and  as  a  rule  the  upper 
valve  should  never  be  open  more  than  a  half  turn  to  a  turn 
more  than  the  lower  valve.  In  all  the  recent  turbines  the 
upper  needle  valve  is  supplied  with  steam  at  pressure  in  Vi  by 
a  pipe  tapped  into  the  primary  valve  chamber,  thus  overcom- 
ing a  tendency  of  the  valves  to  operate  at  light  loads.  The 
secondary  valve  should  begin  to  open  when  the  pressure  below 
the  primary  valve,  that  is  the  inlet  pressure  of  the  turbine, 
is  within  a  few  pounds  of  the  throttle  pressure. 

30 


The  proper  setting  of  the  valves  is  not  a  difficult  matter, 
as  there  may  be  quite  a  wide  variation  in  adjustment  without 
seriously  affecting  the  economy  of  the  machine.  There  are 
two  things,  however,  which  must  be  carefully  looked  out  for. 
First,  that  when  the  governor  is  in  its  highest  position  the 
primary  poppet  valve  will  stop  oscillating  and  remain  solidly 
in  its  seat.  Second,  that  the  machine  can  readily  carry  the 
maximum  load  for  which  it  will  be  called  upon.  The  following 
adjustments  should  therefore  be  carefully  made: 

With  the  governor  clutch  resting  on  the  starting  trigger, 
or  the  mid-position  of  its  travel,  the  turbine  should  be  revolved 
with  just  enough  steam  pressure  to  keep  the  turbine  at  a 
sufficiently  low  speed  to  prevent  the  governor  lifting  off  the 
trigger.  The  primary  relay  plunger  should  then  be  set  so 
that  the  primary  poppet  valve  tends  to  stay  as  far  open  as  the 
steam  pressure  can  keep  it  except  when  the  plunger  reaches 
its  very  lowest  position,  when  the  poppet  valve  should  show  a 
tendency  to  drop  slightly.  If  the  plunger  were  raised  one- 
eighth  of  a  turn  in  the  plunger  head,  the  primary  valve  would 
then  tend  to  stay  as  wide  open  as  possible  during  the  complete 
oscillation  of  the  plunger.  The  plunger,  however,  should  be 
left  in  the  first  position  so  that  whenever  the  turbine  is  started 
up  it  can  be  readily  noticed  that  the  valve  setting  is  correct  by 
the  poppet  valve  having  a  slight  tendency  to  drop  when  the 
plunger  reaches  its  lowest  position  and  the  governor  has  not 
yet  lifted  off  the  trigger. 

In  the  case  of  a  turbine  equipped  with  a  governor  of  the 
type  shown  in  Figure  9,  which  is  not  provided  with  a  trigger, 
the  preliminary  setting  is  made  when  the  turbine  is  tested,  by 
blocking  the  governor  weights  to  bring  the  levers  in  the  posi- 
tion of  mid-travel.  After  the  turbine  has  attained  speed,  any 
further  adjustment  necessary  may  be  made  on  the  relay 
plungers  in  the  manner  described  above. 

Having  made  this  adjustment  of  the  primary  relay 
plunger,  the  turbine  should  then  be  brought  up  to  its  full 
speed  and  in  order  to  check  up  the  setting  the  governor  clutch 
should  be  deliberately  forced  into  its  highest  position  when  the 

31 


32 


primary  poppet  valve  should  stop  beating  and  remain  tight 
shut. 

The  secondary  relay  plunger  is  adjusted  so  that  the 
secondary  poppet  valve  will  admit  steam  to  the  intermediate 
cylinder  of  the  turbine  when  the  average  pressure  below  the 
primary  valve  has  reached  nearly  the  pressure  at  the  throttle. 
This  is  of  course  the  point  when  the  turbine  is  doing  all  the 
work  possible  with  the  primary  valve  open,  and  any  further 
opening  of  the  primary  valve  alone  could  not  admit  any  more 
steam  to  the  machine.  The  secondary  valve  should  open  soon 
enough  so  that  there  will  not  be  too  great  a  drop  in  speed 
before  it  comes  into  play,  the  allowable  drop,  of  course,  depend- 
ing entirely  on  the  nature  of  the  service.  Care  should  be 
taken  in  this  setting  to  prevent  the  valve  from  opening  too 
soon  as  the  economy  of  the  machine  will  be  impaired  if  this 
valve  comes  into  operation  before  the  turbine  is  carrying  the 
maximum  load  possible  with  the  primary  valve  alone. 

Figure  1 1  shows  a  section  of  another  steam  chest  having 
the  same  principle  of  operation  as  the  arrangement  shown  in 
Figure  10,  but  differing  in  the  following  details: 

The  relay  cylinder  and  dash  pot  pistons  instead  of  being 
solid  with  split  packing  rings  are  made  up  of  self-aligning 
sleeves  accurately  turned  to  the  bore  of  the  cylinder  and  pro- 
vided with  small  grooves  to  form  a  labyrinth  packing.  By 
referring  to  the  cut  it  wrill  be  seen  that  on  either  side  of  this 
sleeve  or  ring  are  two  centering  pieces  called  the  upper  and 
lower  dash  pot  pistons,  fitted  on  the  valve  stem,  so  as  to  allow 
a  small  clearance  vertically  as  well  as  sidewise,  thus  avoiding 
the  liability  of  valves  sticking  or  binding  should  the  stem  be 
slightly  out  of  true,  due  to  carelessness  in  assembling. 

Self-aligning  packing  is  also  provided  for  bushing  the 
valve  stem  both  below  the  relay  cylinder  and  at  the  bottom  of 
the  poppet  valve  cage.  This  bushing  is  made  up  of  two  pieces, 
the  lower  one  fitting  the  valve  stem  with  no  more  than  work- 
ing clearance,  and  held  against  a  ground  bevel  seat  on  the 
upper  section  by  means  of  two  springs.  This  provides  very 
nicely  for  a  steam  tight  seal  and  still  permits  of  a  slight  mis- 

33 


alignment  of  the  valve  stem,  without  resultant  binding  or  stick- 
ing of  the  valves. 

The  needle  valves  in  place  of  having  the  seats  bored  in 
the  relay  cylinder  casting  are  provided  with  bronze  bushings 
having  less  tendency  to  cut  from  wiredrawing  and  may  be 
easily  renewed  if  cut  by  wet  steam. 

The  poppet  valve  is  provided  with  a  removable  upper 
disc  and  the  upper  valve  seat  is  also  a  solid  removable  ring 
instead  of  being  made  in  halves  as  formerly.  To  avoid  any 
chance  of  the  primary  valve  spinning,  a  block  with  a  pin 
extending  down  between  the  webs  of  the  valve  is  clamped  on 
the  valve  stem. 

There  is  a  pipe  leading  from  the  chamber  beneath  the 
relay  piston  of  the  primary  valve  to  the  automatic  stop  governor 
valve.  This  is  an  additional  overspeed  safety  device  sup- 
plementing the  automatic  throttle  valve,  as  whenever  the  stop 
governor  operates,  the  chamber  below  the  relay  piston  is 
opened  to  the  atmosphere  regardless  of  the  position  of  the 
relay  plunger,  and  whether  the  automatic  throttle  drops  or  not. 
In  this  manner  the  pressure  is  relieved  from  below  the  piston 
and  the  valve  returned  to  its  seat  by  the  spring.  It  will  be 
noted  that  there  is  a  check  valve  in  this  exhaust  pipe  which 
should  be  kept  tight  so  that  line  pressure  steam  may  not  get 
back  to  interfere  with  the  regulation  of  the  valve. 

The  relay  steam  chest  cylinders  are  extended  and  pro- 
vided with  a  port  connecting  the  relay  plunger  bushing  on 
either  side  of  its  working  ports,  so  that  any  slight  leakage 
may  be  entrapped  and  drained  away  rather  than  bubble  over 
the  steam  chest. 

Oiling  System: 

Mounted  on  the  end  of  the  bedplate  is  the  oil  pump  con- 
nected to  the  turbine  as  previously  explained.  Around  the 
bedplate  are  located  the  oil  cooling  coil,  the  oil  strainer,  the 
oil  reservoir  and  the  oil  piping  to  the  bearings,  etc. 

In  some  machines  of  the  older  types  the  oil  pump  draws 

34 


the  oil  from  the  reservoir,  sending  it  through  the  strainer,  and 
thence  through  the  oil  cooling  coil  located  on  the  side  of  the 
bedplate.  It  will  be  noted  that  there  is  a  by-pass  between  the 
pipes  leading  to  and  from  the  strainer,  and  there  are  valves  in 
these  pipes  so  arranged  that  the  strainer  may  be  cut  out  of  the 
system  and  taken  apart  and  cleaned  while  the  turbine  is 
running  A  spring-loaded  check  valve  in  the  by-pass  auto- 
matically cuts  out  the  strainer,  in  case  it  should  clog  up  to 
such  an  extent  is  to  interfere  with  the  free  circulation  of  the 
oil.  The  strainer  itself  consists  of  a  cast  iron  case  containing 
screens  of  varying  fineness  of  mesh,  the  oil  passing  through 
the  coarsest  first. 

In  later  type  machines  the  strainer  is  located  in  one 
end  of  the  reservoir.  The  oil  returning  from  the  bearings 
flows  through  this  strainer  into  the  reservoir  and  is  then  redis- 
tributed, as  above.  To  clean  this  strainer  while  the  turbine  is 
running,  it  is  only  necessary  to  remove  the  cover  plate  above 
it  and  lift  out  the  several  portions. 

From  the  cooling  coil  the  oil  enters  the  bearing  supply 
pipes,  whence  it  is  led  by  branch  pipes  to  the  several  bearings. 
The  governor  gear  case  acts  as  a  reservoir  to  maintain  the  oil 
at  a  static  head  of  from  one  to  two  feet.  This  is  the  only 
pressure  under  which  the  oil  is  supplied  to  the  bearings.  After 
the  oil  passes  through  the  bearings  it  flows  into  small  reser- 
voirs immediately  under  them,  and  thence  back  to  the  main 
reservoir  under  the  bedplate.  The  oil  is  thus  used  constantly 
over  and  over  again  and  the  only  loss  is  by  deterioration  with 
time,  and  the  very  small  loss  due  to  leakage  and  spilling.  A 
gauge  glass  is  usually  located  in  the  governor  gear  case  to 
indicate  the  level  of  the  oil.  In  certain  types  of  turbines  a 
rotary  pump  is  used  in  place  of  a  plunger  pump  and  the  requi- 
site pressure  is  maintained  on  the  bearings  without  any  oil 
reservoir  in  the  governor  gear  case. 

The  oiling  system  is  somewhat  different  in  cases  where 
an  oil  relay  governor  system  is  employed  for  operating  the 
valve  gear.  In  these  cases  the  main  oil  pump  is  arranged  to 
pump  to  a  higher  pressure  and  it  delivers  oil  directly  to  the 


36 


valve  operating  gear  whence  it  passes  to  the  oil  cooler.  A 
spring  loaded  valve  is  provided  which  allows  the  oil  not 
required  by  the  governor  to  pass  direct  to  the  cooler;  this  valve 
at  the  same  time  maintains  the  pressure  necessary  for  operat- 
ing the  governor  gear. 

In  the  larger  machines  an  auxiliary  oil  pump  is  fur- 
nished. This  pump  is  only  for  the  purpose  of  establishing  a 
circulation  through  the  bearings  with  the  turbine  at  rest,  and 
should  be  cut  out  of  service  as  soon  as  the  turbine  has  reached 
speed  and  the  main  oil  pump  is  maintaining  the  necessary  oil 
pressure.  After  steam  is  shut  off  the  turbine  and  the  speed 
decreases,  the  auxiliary  pump  should  be  started  to  keep  up  the 
oil  supply  to  the  bearings  until  the  turbine  comes  to  rest. 

This  pump  should  be  located  lower  than  the  turbine  so 
that  the  oil  can  run  to  it  by  gravity.  Its  throttle  valve  should 
be  within  easy  reach  of  the  operator  starting  or  stopping  the 
turbine. 

The  oiling  systems  in  different  types  of  machines  vary 
in  their  detailed  arrangements,  but  the  general  principles  are 
as  set  forth  above. 

Automatic  Safety  Stop: 

All  turbines  now  built  are  equipped  with  automatic 
safety  stop  valves  to  shut  down  the  turbine  in  case  the  normal 
speed  is  exceeded  by  a  predetermined  amount.  This  auto- 
matic stop  valve  is  operated  by  a  small  valve  actuated  by  an 
automatic  stop  governor.  The  general  type  of  governor  and 
governor  valve  is  shown  in  Figure  12. 

When  the  speed  of  the  turbine  for  any  reason  rises 
above  normal  and  reaches  a  predetermined  limit,  the  governor 
weight  is  thrown  out  by  centrifugal  force.  This  limit  is  of 
course  fixed  or  adjusted  by  the  compression  put  on  the  gov- 
ernor spring.  The  weight  on  flying  out  comes  in  contact  with- 
a  trigger  cam,  causing  the  trigger  to  disengage  from  the  gov- 
ernor valve  lever,  relieving  the  compression  on  the  governor 
valve  spring,  and  allowing  the  governor  valve  to  open  freely. 
This  exhausts  the  steam  from  the  lower  side  of  a  differential 

37 


38 


piston  on  the  automatic  throttle  stem,  causing  the  throttle  to 
close,  and  shut  off  the  steam  from  the  turbine. 

It  should  also  be  noted  that  the  governor  trigger  may 
be  disengaged  by  hand,  and  the  turbine  shut  down  when 
desired,  by  means  of  the  automatic  stop  valve. 

It  is  expected  that  the  main  turbine  governor  and  inlet 
valve  will  be  kept  in  such  condition  that  the  governor  will 
control  the  speed  at  no  load  under  all  conditions  of  steam 
pressure  and  vacuum.  Nevertheless,  the  automatic  stop  gov- 
ernor and  throttle  valve  should  be  tested  at  frequent  intervals 
to  insure  their  always  being  operative.  Where  a  reliable 
tachometer  or  frequency  meter  is  used,  it  is  well  to  shut  down 
occasionally  by  raising  the  turbine  speed  8%  or  10%  above 
normal,  when  the  automatic  stop  governor  should  come  into 
operation. 

Automatic  Throttle  Valve : 

Figure  13  shows  a  section  of  an  automatic  throttle 
valve,  which  is  placed  in  the  steam  line,  on  the  boiler  side  of 
the  main  throttle  valve,  and  which  is  controlled  by  the  auto- 
matic stop  governor,  just  referred  to. 

Steam  is  shut  off  by  the  piston  D,  which  is  shown  in 
the  figure  as  being  in  the  closed  position.  Steam  from  the 
main  line  passes  up  through  the  valve  D,  and  freely  enters  the 
chamber  M,  above  the  operating  piston,  by  means  of  the 
passage  J.  It  also  leaks  in  limited  quantities  past  the  piston 
and  through  the  bushing  around  the  stem  F,  and  if  prevented 
from  escaping,  accumulates  a  pressure  under  the  piston  E. 
The  stem  K  passes  up  through  the  automatic  throttle  valve 
cylinder  cap,  and  serves  as  an  indicator  to  show  the  position  of 
the  valve.  There  is  no  packing  at  this  point,  so  that  the  pres- 
sure at  P  always  corresponds  to  that  of  the  atmosphere.  The 
opening  C  is  connected  to  the  automatic  stop  governor  valve, 
which,  when  closed,  causes  the  steam  pressure  to  build  up 
under  the  piston  E,  and  the  piston  rises  and  opens  the  valve. 
Should  the  valve  connected  with  C  be  released,  steam  will  be 
exhausted  from  below  the  piston,  and  the  pressure  in  the 
chamber  M  will  force  the  valve  to  the  closed  position. 

39 


40 


There  are  some  packing  rings  on  the  small  diameter  of 
the  operating  piston.  These  are  only  useful  when  the  valve 
is  operating,  or  is  in  the  closed  position.  When  the  valve  is 
open,  which  is  its  normal  position,  these  packing  rings  are  of 
no  value,  as  the  steam-tightness  of  the  parts  is  maintained  by 
the  ground  seat  on  the  piston  N  fitting  against  the  ground 
seat  Q.  To  ensure  against  leakage  of  steam,  it  is  well  to  see 
that  the  piston  has  a  steam  tight  ground  fit  against  the 
shoulder  of  the  valve  stem. 

The  main  valve  D  is  provided  with  two  packing  rings, 
and  in  assembling,  care  should  be  taken  that  these  packing 
rings  are  not  caught  in  the  ports  of  the  valves.  There  is  a 
projection  on  the  valve  cover  to  prevent  the  piston  from  re- 
volving and  getting  the  joints  of  the  packing  rings  in  an  im- 
proper position.  At  G  there  is  a  dowel,  the  function  of  which 
is  to  prevent  the  valve  from  being  assembled  in  such  a  manner 
that  the  steam  may  be  cut  off  from  the  port  J. 

Sometimes,  instead  of  the  automatic  throttle  valve  just 
described,  a  combination  automatic  and  hand  throttle,  of  the 
type  shown  in  Figure  14,  is  employed.  Steam  is  admitted  at 
the  upper  side  of  the  valve  disc,  filling  the  space  above  the 
valve.  By  reason  of  leakage  past  the  balance-piston,  immedi- 
ately above  the  valve  disc,  the  full  pressure  is  established  at  S, 
in  the  balance  cylinder,  which  so  long  as  it  is  maintained, 
tends  to  hold  the  valve  disc  on  its  seat.  On  the  pilot  valve  A 
being  opened,  the  pressure  in  S  is  relieved,  and  the  valve  disc 
then  becomes  approximately  balanced.  The  high  pressure 
steam  entering  the  valve,  freely  passes  into  the  space  L  above 
the  operating  piston,  through  the  ports  Q  and  W.  It  also 
passes  in  limited  quantities  to  the  space  T  below  the  piston, 
both  by  leakage  past  the  piston,  and  leakage  around  the  stem 
R,  so  should  there  be  no  outlet  for  the  steam  at  J,  full  pressure 
will  be  established  at  T,  causing  the  valve  to  open  as  the 
hand  wheel  is  raised,  inasmuch  as  the  upper  portion  of  the 
operating  piston,  where  it  enters  the  dashpot,  is  exposed  to 
atmospheric  pressure  only.  On  the  other  hand,  should  the 
pressure  be  relieved  from  T,  the  valve  will  be  closed  in  a 
manner  similar  to  the  automatic  throttle  valve  previously 

41 


42 


described,  the  port  J,  as  in  the  other  case,  being  connected 
to  the  automatic  stop  governor. 

On  the  upper  portion  of  the  valve  are  the  dashpot  and 
piston,  for  preventing  the  valve  from  slamming  violently  on  its 
seat.  There  is  also  a  valve  position  indicator,  to  show  the  po- 
sition of  the  valve  with  reference  to  its  seat. 

At  P  is  a  metallic  packing  with  a  connection  to  the 
atmosphere,  to  carry  away  any  leakage. 

Provision  is  made  for  locking  the  valve  disc  when  it  is 
in  its  wide  open  position,  so  that  it  may  not  vibrate  or  rattle  in 
the  steam  current.  There  is  also  a  device  to  prevent  the  sud- 
den opening  of  the  valve  after  it  has  automatically  closed, 
should  the  operator  reset  the  automatic  stop  governor,  without 
first  closing  down  the  throttle  valve  hand  wheel.  It  is  thus 
possible  to  readmit  steam  to  the  turbine  with  proper  judgment, 
instead  of  instantaneously  turning  on  the  full  head  of  steam. 
It  is,  of  course,  presupposed  that  there  is  some  derangement  of 
the  governing  gear,  which  has  caused  the  turbine  to  speed  up, 
and  trip  the  safety  stop  mechanism,  so  that  in  starting  the 
turbine  again  care  must  be  taken  to  see  that  the  governor  is  in 
proper  control.  Hence  the  desirability  of  speeding  up  the  tur- 
bine somewhat  slowly  and  not  exposing  it  instantaneously  to 
the  full  head  of  steam. 

This  is  accomplished  by  holes  through  the  operating 
piston  at  G,  and  a  spring  loaded  valve  called  the  cylinder 
exhaust  valve,  located  in  the  upper  portion  of  the  operating 
piston.  The  lower  side  of  this  valve  is  exposed  to  the  full 
pressure,  which,  however,  is  insufficient  to  compress  the  spring. 
On  the  valve  being  opened,  the  valve  disc  fetches  up  against 
the  body  head.  The  upper  stem,  however,  has  a  little  further 
to  travel  before  the  head  on  the  lower  end  of  it  is  stopped 
against  the  bushing  on  the  upper  pcrtion  of  the  dashpot. 
This  permits  the  cylinder  exhaust  valve  spring  to  expand  a 
trifle,  but  still  not  sufficient  for  the  steam  pressure  to  force 
open  the  valve  D;  this  feature  of  the  valve  disc,  being  held  by 
the  operating  piston  tightly  against  the  valve  body  head,  is 
what  prevents  the  valve Jfrom  rattling  in  the  current  of  steam. 

43 


44 


Should  the  valve  close  automatically,  the  operating  piston  with 
the  cylinder  exhaust  valve,  will  descend  leaving  the  upper 
throttle  valve  stem,  when  the  spring  will  be  entirely  released, 
and  the  valve  D  will  be  free  to  open.  Then,  should  the  auto- 
matic stop  governor  valve  be  closed  at  this  time,  thus  prevent- 
ing egress  of  steam  at  J,  it  will  be  impossible  for  the  steam 
pressure  to  build  up  at  T,  because  the  steam  will  be  free  to 
escape  through  the  holes  G,  the  valve  D,  and  the  sight  hole  N. 
Hence  the  valve  will  be  unable  to  open  until  the  hand  wheel 
has  been  screwed  down,  forcing  the  cylinder  exhaust  valve  D 
to  the  seat. 

In  opening  the  valve,  the  upper  valve  stem  on  being 
raised,  permits  the  operating  piston  to  first  open  the  pilot 
valve  A,  relieving  the  steam  in  S,  thus  practically  balancing 
the  throttle  valve  itself,  after  which  the  operating  piston  is 
capable  of  opening  the  main  valve  in  the  manner  before 
described. 

Coupling: 

The  coupling  between  the  turbine  rotor  and  the  gener- 
ator field  shaft  is  either  of  the  sleeve  type  or  of  the  claw  type. 

The  former  is  used  on  turbines  of  small  capacity  and 
high  speed.  In  this  case  the  coupling  ends  of  the  turbine  and 
generator  shafts  are  machined  square,  and  the  coupling  is  a 
steel  cylinder  slotted  out  to  fit  with  sufficient  clearance  to  allow 
it  to  slide  freely  on  the  squares.  This  coupling  should  be  free 
to  slide  easily  on  the  shafts,  both  when  turbine  is  cold  and 
when  it  is  heated  to  operating  conditions. 

The  claw  coupling  employed  on  the  larger  machines  is 
shown  in  Figs.  15  and  16.  The  sleeves  are  pressed  on  the  ends 
of  the  shafts,  and  secured  by  the  keys  K  K.  They  are  then 
turned  true,  a  narrow  shoulder  being  left  near  the  fingers  on 
which  the  coupling  head  fits  freely  with  a  slight  clearance. 
The  smaller  diameter  at  the  ends  of  sleeves  C  C  allows  some 
flexibility. 

Oil  grooves  H  are  cut  in  the  driving  faces  of  the  fingers 
on  the  coupling  head  and  are  supplied  with  oil  thrown  off  the 

45 


shaft  and  caught  in  the  retaining  ring  D.  This  is  a  split  oil 
ring  held  on  the  head  by  bolts  T  and  has  oil  holes  which  reg- 
ister with  the  grooves  on  the  coupling  fingers.  On  assembling, 
care  should  be  taken  that  the  rings  are  placed  so  that  the  oil 
holes  correspond  to  the  grooves  in  the  fingers,  and  that  they 
are  free  from  foreign  matter  that  might  restrict  the  oil  passages. 
The  retainer  rings  also  serve  to  restrict  the  end  motion 
of  the  revolving  field  and  prevent  the  shoulders  on  the  shaft 
from  coming  in  contact  with  the  ends  of  the  bearings. 


46 


IV. 
Operating  Suggestions. 

Before  putting  the  turbine  into  operation  for  trie  first 
time,  it  should  be  completely  dismantled  and  the  spindle  re- 
moved so  that  an  inspection  may  be  made  of  all  of  the  parts, 
to  insure  that  they  have  suffered  no  injury  in  transit.  The 
bearings,  valve  gear  and  governor  parts  should  be  carefully 
inspected  and  cleaned.  The  oil  tanks  and  pedestal  reservoirs 
should  be  thoroughly  cleaned,  and  particular  care  should  be 
taken  that  the  gland  overflow  drain  is  clear,  as  should  this 
become  clogged,  any  water  that  might  leak  through  the  glands 
would  pass  into  the  oiling  system.  The  pilot  valves  should  be 
removed  and  the  bushings  cleaned. 

After  the  turbine  has  been  reassembled,  the  oiling  sys- 
tem should  be  filled  either  by  pouring  the  oil  into  the  governor 
gear  case  G,  Fig.  2  — if  this  type  of  governor  is  used — or  by 
means  of  the  pipe  and  funnel  provided  in  connection  with 
the  oil  reservoir.  Bnough  oil  should  be  provided  so  that  when 
the  turbine  is  running  at  full  speed,  the  suction  to  the  pump 
is  covered,  and  no  air  is  drawn  into  the  system.  Although 
there  is  a  strainer  in  the  oiling  system,  it  is  well,  as  a  matter 
of  precaution,  to  strain  the  oil  either  before  putting  it  into  the 
turbine,  or  to  pour  it  into  the  reservoir  through  a  fine  mesh 
screen  or  cloth. 

Before  connecting  the  steam  line  to  the  turbine  inlet, 
the  whole  line  clear  back  to  the  boilers  should  be  blown  out 
with  live  steam  to  remove  all  scale  from  the  pipe,  as  well  as 
any  other  foreign  matter  that  might  have  been  left  in  the  pip- 
ing during  erection.  There  is  a  steam  strainer  in  the  inlet  at 
S,  Fig.  2,  but  fine  sand  and  particles  of  gasket  might  pass 
through  and  choke  up  the  first  row  of  blades,  restricting  the 
steam  passage  to  some  extent. 

Care  and  judgment  must  be  exercised  in  the  warming 
up  of  the  turbine  before  starting,  as  it  is  quite  possible  to  over 
do  it,  particularly  where  steam  is  superheated.  If  it  were 


possible  to  warm  the  turbine  evenly  all  over,  it  could  not 
become  overheated  before  starting,  but  so  long  as  the  turbine 
is  standing  still,  this  is  impossible.  With  small  quantities  of 
steam  passing  through  the  turbine,  the  hottest  steam  will 
remain  above,  falling  to  the  lower  portion  as  it  is  cooled,  with 
the  natural  resiilt  that  neither  the  spindle  nor  the  cylinder  will 
be  straight,  the  former  running  out  of  true  as  soon  as  it  is 
revolved.  It  is,  therefore,  the  better  practice  to  warm  the 
turbine  only  moderately  and  get  it  revolving  as  quickly  as 
possible,  and  really  do  the  latter  part  of  the  warming  up  after 
the  machine  is  in  motion.  The  higher  the  superheat  the  more 
important  it  is  that  the  machine  be  not  allowed  to  stand  for  a 
long  time  with  steam  blowing  through  it. 

The  turbine  should  be  started  up  non-condensing  and 
not  subjected  to  vacuum  until  it  has  attained  sufficient  speed  to 
allow  the  water  glands  to  effectively  seal.  The  reason  for  this 
precaution  is  that  if  a  vacuum  were  established  in  the  condenser 
or  even  the  air  pump  operated  with  the  turbine  at  rest,  or 
before  the  glands  were  packed,  a  certain  amount  of  air  would 
be  drawn  into  the  casing  at  both  ends  of  the  spindle,  which 
would  result  in  some  distortion  of  the  spindle,  causing  it  to 
run  out  of  true  until  such  time  as  it  had  become  evenly  heated 
throughout  its  length.  When  there  is  no  gate  valve  between 
the  turbine  and  condenser,  some  means  of  forced  injection 
must  be  provided  so  that  the  turbine  can  be  started  non-con- 
densing and  the  vacuum  established  afterwards. 

This  general  rule,  of  course,  does  not  apply  to  low 
pressure  turbines,  which  are  treated  of  in  a  special  pamphlet. 

After  the  turbine  is  up  to  speed  and  under  control  of 
the  governor,  it  is  well  to  make  sure  that  the  speed  is  correct, 
either  by  counting  the  strokes  of  the  governor  vibrator,  or  by 
noting  the  tachometer,  if  there  is  one,  as  it  is  possible  that  the 
adjustment  of  the  governor  may  have  been  interfered  with 
while  the  machine  was  standing  idle.  It  is  also  well  at  this 
time,  while  there  is  no  load  on  the  turbine,  to  be  sure  that  the 
governor  controls  the  machine  with  a  high  vacuum  and  the 
throttle  wide  open.  It  might  be  that  the  main  poppet  valve 

48 


was  leaking  or  that  it  had  sustained  some  injury  not  evident 
when  the  inspection  was  made.  The  action  of  the  valve  and 
the  control  of  the  governor  should  be  noted  each  time  the 
turbine  is  started  or  shut  down,  and  should  there  be  any  such 
defect,  steps  should  be  taken  to  regrind  the  valve  to  its  seat  at 
the  first  opportunity,  as  a  small  leak  will  rapidly  become  seri- 
ous through  wiredrawing  the  steam. 

Where  conditions  will  permit,  it  is  better  to  build  up  the 
load  gradually  so  that  there  may  be  no  sudden  heavy  demand 
upon  the  boilers  with  the  possibility  of  water  being  drawn  over 
into  the  turbine.  While  there  is  110  danger  of  the  serious 
results  that  are  almost  certain  to  occur  in  a  reciprocating 
engine,  a  slug  of  water  is  by  no  means  desirable,  as  it  will 
cause  the  turbine  speed  to  decrease  considerably  and  impose 
undue  strains  on  the  machine.  Care  should  be  taken  both  in 
the  arrangement  of  the  piping  and  in  the  method  of  operation 
to  avoid  any  sudden  rush  of  water  to  the  turbine,  especially  in 
case  superheated  steam  is  used. 

It  should  hardly  be  necessary  to  state  that  while  the 
turbine  is  running  it  should  be  given  the  same  careful  and 
systematic  attention  demanded  by  any  high  class  engine.  That 
is,  at  regular  intervals  the  engineer  should  inspect  and  note 
the  temperature  of  bearings  and  oiling  system,  the  water 
pressure  on  the  glands,  pressure  of  steam  and  action  of  governor 
and  valves.  Should  any  irregularity  be  detected,  such  as 
loss  of  gland  water  or  insufficient  oil  supply,  he  should  im- 
mediately locate  the  cause  and  correct  it. 

No  alarm  should  be  felt  if  the  turbine  bearings  are  very 
warm,  as  there  is  no  danger  as  long  as  the  hand  can  be  borne 
on  them  even  momentarily.  However,  should  a  bearing  show 
signs  of  distress,  as  evidenced  b}^  smoke  or  burning  oil,  the 
trouble  should  be  investigated  immediately  without  attempt- 
ing to  nurse  it  back  into  condition.  These  bearings  are  subject 
to  a  continuous  circulation  of  oil,  and  should  give  no  trouble, 
and  if  a  bearing  starts  to  burn,  there  is  some  definite  cause  for 
it,  such  as  a  stoppage  of  oil  supply,  foreign  matter  in  the  oil, 
or  a  tight  bearing  cap,  and  the  cause  should  be  removed  with- 

49 


out  delay.  In  case  superheated  steam  is  used,  the  thermome- 
ter should  be  read  at  intervals  in  order  to  make  sure  that  the 
turbine  is  not  being  subjected  to  excessive  variations  of  tem- 
perature. 

While  accidents  to  blading  are  of  infrequent  occnrrence 
and  not  to  be  expected  tinder  normal  operating  conditions, 
should  any  sound  of  rubbing  or  grinding  be  detected,  the  tur- 
bine shonld  be  shut  down  immediately,  and  the  trouble  located 
and  rectified  before  any  serious  damage  results.  The  engineer 
should  not  be  misled  by  thinking  any  nnusual  sound  too 
trivial  to  warrant  investigation.  Every  irregularity  should  be 
looked  into  at  once  and  in*  this  way  serious  results  may  be 
averted.  It  is  possible  that  after  inspection,  the  bearing  align- 
ment may  have  been  changed  inadvertently,  and  the  blade 
clearance  decreased.  Should  any  blades  be  damaged,  and 
should  there  be  insufficient,  time  to  make  a  proper  repair,  the 
turbine  may  be  put  back  into  service  if  the  damaged  blades  are 
removed.  If  any  considerable  portion  of  any  blade  row  is 
damaged,  the  entire  row  should  be  removed.  As  the  blade 
rows  are  in  pairs — one  stationary  and  one  moving — not  only 
must  the  damaged  row  be  removed,  but  also  the  correspond- 
ing moving  or  stationary  row  that  in  connection  with  the 
damaged  row  makes  a  complete  pair — unless  a  complete  pair 
of  rows  is  removed,  the  end  thrust  of  the  rotor  will  be  unbal- 
anced. The  turbine  will  operate  at  some  small  sacrifice  of 
economy  until  such  time  as  it  is  convenient  to  make  a  proper 
repair. 

When  a  turbine  is  first  put  into  service  the  oil  strainers 
should  be  removed  after  a  few  hours'  run  and  cleaned  of  any 
foreign  matter  that  may  have  found  its  way  into  the  oiling 
system.  After  the  first  few  days'  run,  when  the  oil  circulation 
has  washed  out  the  system,  as  it  were,  such  frequent  cleanings 
of  this  strainer  should  not  be  necessary,  and  the  amount  of 
dirt  found  will  indicate  how  often  it  is  advisable  to  take  care  of 
it.  The  strainer  may  be  removed  while  the  turbine  is  in  opera- 
tion, as  explained  in  the  description  of  the  oiling  system. 


50 


Frequent  and  sudden  changes  from  condensing  to  non- 
condensing  operation  with  the  turbine  under  load  should  be 
avoided.  Should  it  be  necessary  to  cut  out  the  condenser,  the 
vacuum  should  be  reduced  as  slowly  as  the  existing  conditions 
will  allow,  so  that  no  stresses  may  be  set  up  in  the  turbine 
casing,  by  reason  of  sudden  changes  of  temperature  in  the 
exhaust  end. 

In  shutting  down  the  turbine,  the  vacuum  should  be 
broken  as  soon  as  the  turbine  throttle  is  closed  so  that  as 
the  turbine  comes  to  rest,  cold  air  will  not  be  drawn  in  through 
the  glands  on  the  heated  spindle.  Also  do  not  leave  the  gland 
water  running,  as  it  may  leak  over  into  the  bearing  and 
pedestal  reservoirs. 

As  is  customary  with  engines  of  any  type,  the  turbine 
should  be  completely  dismantled  and  inspected  every  year. 
The  word  dismantled  is  used  in  its  fullest  sense,  and  means 
that  the  rotor,  valves,  bearings,  oil  cooling  coil,  etc.,  should  all 
be  removed.  If  the  valves  show  any  sign  of  cutting  they 
should  be  ground  to  their  seats.  The  cooling  coil  may  show 
a  deposit  from  the  oil  on  one  side  or  water  on  the  other  side, 
thus  interfering  with  the  circulation  of  the  oil  and  effectiveness 
of  the  cooling  surface.  If  the  bearings  or  coils  show  an  exces- 
sive oil  deposit,  the  brand  of  oil  should  be  looked  into,  as  in 
time  the  piping  may  become  clogged  up,  imperiling  the  safety 
of  bearings  by  restricting  the  oil  supply. 

The  governor  should  be  cleaned  and  inspected  and  the 
knife  edge  pins  examined  to  make  sure  that  no  grit  has  found 
its  way  to  them,  causing  wear  which  would  injuriously  affect 
the  sensitive  action  of  the  governor. 

The  glands  and  balance  pistons  should  be  examined  for 
any  deposit  of  lime  from  hard  water,  as  discussed  later  in  the 
explanation  of  the  several  methods  of  gland  piping.  Also  the 
blading  should  be  carefully  inspected,  and  in  case  there  is  any 
deposit  of  mud  or  scale  from  the  boilers,  it  should  be  cleaned 
out  and  steps  taken  to  prevent  a  renewal  of  this  condition. 

During  an  inspection  it  is  always  desirable  to  check  up 
the  clearance  over  the  tips  of  the  blades.  This  is  accomplished 

51 


by  removing  liners  one  by  one  from  behind  the  keys  on  the 
under  side  of  the  main  bearings,  (see  H,  Fig.  6.)  This  allows 
the  spindle  to  be  lowered  in  the  cylinder,  a  distance  equal  to 
the  thickness  of  the  liners  removed.  Several  trials  should  be 
made,  removing  additional  liners  at  each  trial,  and  revolving 
the  spindle  by  hand  until  the  tips  of  the  blades  just  begin  to 
rub.  As  the  liners  are  of  known  thickness  expressed  in 
thousandths  of  an  inch,  the  clearance  can  be  obtained  with 
great  exactness. 

In  a  similar  manner  the  spindle  may  be  raised  above  its 
original  position,  and  the  top  clearance  determined;  it  may 
then  be  moved  sidewise  in  either  direction  and  the  side  clear- 
ances measured. 

From  the  measurement  of  liner  thicknesses,  the  spindle 
may  readily  be  set  in  any  desired  position  in  the  cylinder.  It 
is  customary  to  set  it  some  few  thousandths  above  the  central 
position,  the  exact  amount  differing  somewhat  according  to  the 
size  and  type  of  the  machine.  It  is  always  desirable  to  have 
the  clearances  such  that  the  spindle  blades  will  rub  on  the 
walls  of  the  cylinder  before  the  cylinder  blades  rub  on  the  sur- 
faces of  the  spindle,  as  in  the  event  of  blades  striking  while 
the  turbine  is  running  the  rubbing  is  less  harmful. 


52 


V. 
Condensers. 

While  the  choice  of  the  condenser  is  a  matter  of  special 
engineering  and  hardly  within  the  province  of  this  pamphlet, 
the  economy  of  the  tnrbine  is  so  dependent  on  the  condenser 
performance,  that  a  few  remarks  on  this  snbject  will  not  be 
out  of  place. 

So  far  as  the  turbine  is  concerned,  one  type  of  conden- 
ser is  as  good  as  another.  The  condenser  which  will  give  the 
best  performance,  regarded  from  the  standpoint  of  condenser 
performance  only,  is  the  best  one  to  use.  The  condenser 
should  be  such  that  it  will  carry  the  highest  vacuum  con- 
sistent with  the  temperature  and  volume  of  cooling  water 
available,  and  the  choice  of  type  depends  largely  upon  the 
individual  conditions  of  the  plant. 

Where  a  condenser  capable  of  giving  the  highest 
vacuum  is  installed,  the  need  of  utilizing  this  capability  to  the 
utmost,  can  hardly  be  emphasized  too  strongly.  A  high 
vacuum  will,  of  course,  entail  special  care  and  attention  and 
constant  guarding  against  air  leaks  in  the  exhaust  piping,  but 
it  will  result  in  the  most  economical  operation  of  the  turbine. 
It  must  not  be  inferred  that  a  high  vacuum  is  essential  to  suc- 
cessful operation  of  the  turbine,  for  most  satisfactory  results 
are  obtained  with  low  vacuum  and  even  without  any  at  all. 
However,  as  it  is  a  well  known  fact  that  the  steam  economy  of 
a  turbine  with  high  vacuum  increases  in  greater  proportion 
than  that  of  a  reciprocating  engine,  the  condenser  should  be 
kept  at  its  highest  efficiency,  in  order  that  full  advantage  may 
be  taken  of  this  feature. 


53 


VI. 
Oils. 

There  are  several  oils  on  the  market  that  are  suitable 
for  use  in  the  turbine  oiling  system,  but  great  care  must  be 
taken  to  select  a  proper  one.  In  the  first  place,  the  oil  must 
be  pure  mineral,  unadulterated  with  either  animal  or  vegetable 
oils,  and  must  have  been  washed  free  from  acid.  Certain 
brands  of  oil  require  the  use  of  sulphuric  acid  in  their  manu- 
facture and  are  apt  to  contain  varying  degrees  of  free  acid  in 
the  finished  product.  A  sample  from  one  lot  may  have  almost 
no  acid,  while  one  from  another  lot  may  contain  a  dangerous 
amount. 

Mineral  oils  that  have  been  adulterated  will,  when 
heated  up,  partially  decompose,  forming  acid.  These  oils  may 
be  very  good  lubricants  when  first  put  into  use,  but  after  a 
while  they  lose  all  their  good  qualities  and  become  harmful 
to  the  machine  by  corroding  the  journals  in  which  they  are 
used.  These  oils  must  be  very  carefully  avoided  in  the 
turbine,  as  the  cheapness  of  their  first  cost  will  in  no  way  pay 
for  the  damage  they  may  do.  A  very  good  and  simple  way  to 
test  for  such  adulterations  is  to  shake  up  a  quantity  of  the 
oil  in  a  test  tube  with  a  solution  of  borax  and  water.  If  there 
is  any  animal  or  vegetable  adulterant  present  it  will  appear  as 
a  white,  milk-like  emulsion,  which  will  not  separate  out  when 
allowed  to  stand.  The  pure  mineral  oil  will  appear  at  the  top 
as  a  clear  liquid,  and  the  excess  of  the  borax  solution  at  the 
bottom,  the  emulsion  being  in  between.  A  number  of  oils  also 
contain  a  considerable  amount  of  paraffine  which  is  deposited 
in  the  oil  cooling  coil,  preventing  the  oil  from  being  cooled 
properly,  and  in  the  pipes  and  bearings,  choking  the  oil 
passages  and  preventing  the  proper  circulation  of  the  oil  and 
the  cushioning  effect  in  the  bearing  tubes.  This  is  not  entirely 
a  prohibitive  drawback,  the  chief  objection  being  that  it  neces- 
sitates an  unduly  frequent  cleaning  of  the  cooling  coil,  oil 
piping  and  bearings. 


54 


Some  high  class  mineral  oils  of  high  viscosity  are 
inclined  to  emulsify  with  water,  the  emulsion  appearing  as  a 
jelly-like  substance.  It  might  be  added  that  oils  having  a 
high  viscosity  are  not  the  most  suitable  for  turbine  use. 

Since  the  consumption  of  oil  in  a  turbine  is  so  very 
small,  being  practically  only  that  due  to  leakage  or  spilling, 
the  price  paid  for  it  should  be  of  secondary  importance;  the 
prime  consideration  should  be  its  suitability  for  the  purpose. 

In  some  cases  a  central  gravity  system  will  be  employed, 
instead  of  the  oil  system  furnished  with  the  turbine,  which,  of 
course,  will  be  a  special  consideration . 

For  large  installations  a  central  gravity  oiling  system 
has  much  to  recommend  it,  but  as  it  performs  such  an  impor- 
tant function  in  the  power  plant  and  its  failure  would  be  the 
cause  of  so  much  damage,  every  detail  in  connection  with  it 
should  be  most  carefully  thought  out,  and  designed  with  a 
view  that  under  no  combination  of  circumstances  would  it  be 
possible  for  the  system  to  become  inoperative.  One  of  the 
great  advantages  of  such  a  system  is  that  it  can  be  designed  to 
contain  very  large  quantities  of  oil  in  the  settling  tanks,  and 
the  oil  will  thus  have  quite  a  long  rest  between  the  times  of 
its  being  used  in  the  turbine,  a  circumstance  which  seems  to 
be  very  helpful  in  extending  the  life  of  the  oil.  We  further- 
more believe  that  where  the  oil  can  have  a  long  rest  for  set- 
tling, an  inferior  grade  of  oil  may  be  used,  providing,  however, 
that  it  is  absolutely  free  from  acid. 

We  will  at  all  times  be  glad  to  co-operate  with  engin- 
eers installing  our  turbines  and  consult  with  them  as  to  the 
design  of  oiling  systems. 


55 





JL,& 


A  -.  & 

fl^iSH 


*  &, 


METHOD  OF 
MAKING  WATER 
CONNECTIONS  TO 
GLANDS  AND 
OIL  COOLING 
COILS. 


Fig.  17 


56 


VII. 
Methods  of  Connecting  up  Glands  and   Oil  Cooling  Coils. 

Theue  are  several  satisfactory  plans  of  connecting  the 
water  supply  to  the  glands  and  oil  cooler,  the  choice  of  any 
certain  one  depending  upon  the  particular  conditions  existing 
in  the  power  house. 

The  temperature  of  the  water  for  the  gland  supply  must 
be  lower  than  the  temperature  of  the  steam,  due  to  the  vacuum 
in  the  turbine,  or  it  will  evaporate  rapidly  and  find  its  way 
into  the  turbine  in  the  form  of  steam. 

In  any  case,  a  small  amount  of  the  sealing  water  will 
pass  by  the  gland  collars  into  the  turbine  so  that,  if  the  con- 
densed steam  be  returned  to  the  boilers,  the  water  used  in  the 
glands  must  be  of  such  character  that  it  will  not  be  injurious 
to  the  boilers.  Whether  the  water  so  used  is  returned  to  the 
boilers  or  not,  it  should  never  contain  an  excessive  amount  of 
lime  or  solid  matter,  as  some  evaporation  is  continually  going 
on  in  the  glands  which  will  cause  the  deposit  of  scale,  and 
necessitate  frequent  disassembling  for  cleaning.  If  the  scale 
is  allowed  to  form,  it  will  be  deposited  on  the  back  of  the 
balance  piston,  throwing  the  machine  out  of  balance.  There 
is  also  danger  of  its  filling  up  the  space  in  which  the  gland 
runners  work  to  such  an  extent  as  to  cause  mechanical  contact 
which  may  produce  serious  vibrations. 

In  the  following  pages  are  described  various  plans  for 
supplying  water  to  the  glands  and  oil  cooler,  and  it  is  believed 
these  cover  all  of  the  conditions  that  are  ordinarily  met  with. 

First: 

Where  there  is  a  cheap  supply  of  good  pure  water,  the 
same  water  that  is  used  in  cooling  the  oil  may  be  utilized  for 
the  glands.  The  discharge  from  the  cooling  chamber  is  run 
to  a  stand  pipe  with  a  height  of  10  feet  above  the  axis  of  the 
glands  and  the  supply  to  the  glands  is  taken  through  a  T  just 

57 


outside  of  the  cooling  chamber,  as  shown  diagrammatically  at 
A,  Figure  17.     This  is  the  method  generally  employed. 

The  quantity  of  water  required  for  the  oil  cooler  is 
always  more  than  sufficient  for  the  glands. 

Second: 

Where  there  is  a  limited  supply  of  proper  water  for  the 
glands  and  a  large  and  cheap  supply  of  poorer  water  which 
may  be  readily  used  in  the  oil  cooling  chamber,  the  cooling 
chamber  and  the  glands  will  be  piped  up  separately,  each  to 
its  own  supply,  the  oil  cooling  supply  discharging  through  the 
cooler,  direct  into  the  sewer  or  similar  waste.  The  glands 
will  then  be  supplied  from  a  pure  water  supply,  this  supply 
pipe  having  a  branch  to  the  glands  and  being  led  to  a  stand 
pipe,  the  overflow  from  which  discharges  into  the  hot  well> 
serving,  if  desired,  for  "make  up  feed,"  as  in  B,  Figure  17. 
In  this  case  it  is  possible  to  take  the  water  for  the  glands  from 
the  feed  line  at  a  point  between  the  pump  and  the  feed  heater, 
and  discharge  it  from  the  gland  overflow  into  the  tank  to 
which  the  suction  of  the  feed  pumps  is  connected. 

Third: 

When  the  only  available  supply  of  pure  water  is  that 
for  the  boiler  feed  and  the  condensed  steam  is  pumped  directly 
back  to  the  boiler,  as  is  shown  at  C,  Fig.  17,  then  the  delivery 
from  the  condensed  water  pump  may  deliver  to  an  elevation 
10  feet  above  the  axis  of  the  glands,  where  a  tank  should  be 
furnished  of  sufficient  capacity  that  the  water  may  have  time 
to  cool  considerably  before  being  delivered  to  the  glands. 

In  most  of  these  cases,  if  desired,  the  oil  cooling  water 
may  come  from  the  circulating  pump  for  the  condenser,  pro- 
viding there  is  sufficient  pressure  to  produce  circulation. 

Fourth: 

The  arrangement  B  may  be  somewhat  costly  if  the 
water  fed  to  the  glands  has  to  be  brought  from  the  city  water 
mains  and  cannot,  after  service  in  the  glands,  be  made  good 
use  of,  as  opening  the  supply  too  wide  will  allow  most  of  the 


water  to  go  into  the  overflow  which,  in  some  cases,  may  exceed 
the  quantity  necessary  for  make-up  boiler  feed,  and  is,  there- 
fore, liable  to  be  wasted.  The  arrangement  shown  diagram- 
matically  at  D  admits  just  enough  and  no  more  water  than  is 
necessary  for  sealing  the  glands.  This  method  is  probably  the 
one  which  is  the  most  economical  of  water.  One  tank  can  obvi- 
ously furnish  required  water  pressure  to  any  number  of  tanks  in 
the  same  station.  This  type  of  tank  is  one  which  can  be  bought 
in  plumbers'  stores,  and  is  such  as  is  used  for  toilet  rooms,  etc. 

Fifth: 

In  certain  cases  the  turbine  is  required  to  exhaust 
against  a  back  pressure  of  one  or  two  pounds,  when  a  slightly 
different  arrangement  of  piping  must  be  made.  The  sealing 
water  in  this  case  must  be  allowed  to  circulate  through  the 
glands  in  order  to  keep  the  temperature  that  is  within,  below 
212  degrees  Fahrenheit.  If  this  is  not  done  the  water  in  the 
glands  will  become  heated  from  the  main  castings  of  the 
machine  and  will  evaporate.  This  evaporation  will  make  the 
glands  appear  as  though  they  were  leaking  badly.  In  reality 
it  is  nothing  more  than  the  boiling  of  water  in  the  glands,  but 
it  is,  nevertheless,  equally  objectionable. 

E,  Fig.  17,  illustrates  a  method  of  overcoming  this 
objectionable  feature  where  the  general  arrangement  may  be 
the  same  as  any  one  of  the  se'/eral  methods  proposed,  except 
that  two  connections  and  valves  are  furnished  at  M  and  N, 
which  drain  away  to  any  suitable  tank  or  sewer.  These  valves 
are  open  just  enough  to  keep  sufficient  circulation  to  keep  the 
temperature  of  the  gland  water  below  the  boiling  point,  boiling 
being  evidenced  by  steam  coming  out  of  the  glands  as  though 
they  w~ere  leaking. 

In  case  the  turbine  is  operating  against  back  pressure 
the  water  pressure  on  the  glands  must  be  raised  above  the 
standard  of  five  pounds  by  the  amount  that  the  back  pressure 
exceeds  the  pressure  of  the  atmosphere.  That  is  to  say,  in 
case  a  back  pressure  of  five  pounds  gauge  is  maintained,  a 
gland  pressure  of  ten  pounds  or  a  standpipe  about  twenty  feet 
above  the  axis  would  be  required. 


<9H 


&  i 


VIII. 
Foundations. 

The  foundations  should  be  built  in  accordance  with  the 
requirements  called  for  in  the  official  foundation  plans. 

These  drawings,  however,  are  not  intended  to  give  the 
actual  design  of  the  foundation,  as  this  must  be  made  to  suit  the 
particular  conditions  of  the  individual  power  house.  Its  design 
is  not  limited  like  that  for  a  reciprocating  engine,  and  hence 
can  be  made  in  many  ways,  to  suit  the  arrangement  of  con- 
densers and  auxiliary  apparatus  in  the  basement,  as  well  as 
any  peculiarities  of  building,  etc.  As  the  motion  of  the  tur- 
bine is  rotary,  it  is  not  necessary  to  provide  heavy  foundations 
or  any  foundation  bolts,  but  at  the  same  time  it  is  necessary  to 
provide  a  foundation  such  that  any  part  of  it  will  support  its 
share  of  the  weight  of  the  turbine  and  generator  without  sink- 
ing, and  consequently  disturbing  the  alignment  of  the  machine. 
In  designing  the  foundation,  provision  should  be  made 
for  the  necessary  air  ducts  for  ventilating  the  generator,  and 
one  inch  of  grout  should  always  be  allowed  for  on  top  of  the 
foundation. 

While  concrete  is  to  be  preferred  wherever  practicable 
it  is  often  convenient  to  install  the  turbine  on  a  structural 
steel  floor  because  of  the  greater  amount  of  space  left  in  the 
basement  for  auxiliary  apparatus.  In  order  that  such  a  floor 
may  be  sufficiently  rigid,  and  to  avoid  the  location  of  beams  in 
positions  where  they  would  interfere  with  proper  access  to  the 
turbine,  we  show  on  our  foundation  plan  a  desirable  arrange- 
ment of  beams.  We  also  specify  the  size  of  beams  required 
for  various  spans  in  order  that  the  deflection  may  be  kept 
down  to  .020,  which  is  considered  to  be  as  great  a  deflection 
as  should  be  allowed.  In  using  a  structural  steel  floor,  it  is 
very  convenient  to  run  in  one-half  to  one  inch  of  lead  between 
the  turbine  bedplate  and  the  steel  work,  so  that  the  turbine 
may  be  properly  leveled  with  the  weight  evenly  distributed  on 

61 


all  beams,  as  there  is  liable  to  be  some  slight  misalignment  in 
the  steel  work.  This  lead  pad  also  tends  to  absorb  any  slight 
vibration  that  may  exist.  With  either  a  structural  steel  or 
concrete  foundation  the  final  leveling  should  not  be  done  until 
the  entire  weight  of  the  turbine  and  generator  is  in  place,  after 
which  the  lead  or  grout  may  be  poured. 

As  before  stated  the  concrete  foundation  is  more  desir- 
able, as  any  vibration  tends  to  be  intensified  if  the  turbine  is 
mounted  on  structural  steel,  and  especially  is  this  the  case  if 
any  members  form  a  harmonic  with  the  turbine  vibration. 
A  desirable  and  convenient  form  of  foundation  is  shown  in 
Fig.  18. 


The  Westinghouse  Machine  Co. 

General  Offices  and  Works 

East  Pittsburg,  Pa. 


New  York 
Atlanta 
Boston 
Chicago 
Cincinnati 
Cleveland 
San  Francisco 
Denver 
Pittsburg 
Philadelphia  - 
St.  Louis 
City  of  Mexico 


SALES  OFFICES 

165  Broadway 

Candler  Building 

131  State  Street 

171  La  Salle  Street 

1102  Traction  Building 

New  England  Building 

Hunt,  Mirk  &  Co.,  141  Second  Street 

512  McPhee  Building 

Westinghouse  Building 

1003  North  American  Building 

Chemical  Building 

-      G.  and  O.  Braniff  &  Co. 


STAMPED  BELOW 


AN  INITIAL  FINE  OF  25  CENTS 

WILL  BE  ASSESSED  FOR  FAILURE  TO  RETURN 
THIS  BOOK  ON  THE  DATE  DUE.  THE  PENALTY 
WILL  INCREASE  TO  SO  CENTS  ON  THE  FOURTH 
DAY  AND  TO  $1.OO  ON  THE  SEVENTH  DAY 
OVERDUE. 


11  19E 


LD  21-100m-7,'39(402s) 


726306 


lA/4 


UNIVERSITY  OF  CALIFORNIA  LIBRARY 


